EP0022729B1 - Bistabiles hydraulisches Ventil für die Steuerung eines Kolbens eines schnellen Hochspannungs-Leistungsschalters - Google Patents

Bistabiles hydraulisches Ventil für die Steuerung eines Kolbens eines schnellen Hochspannungs-Leistungsschalters Download PDF

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Publication number
EP0022729B1
EP0022729B1 EP19800401062 EP80401062A EP0022729B1 EP 0022729 B1 EP0022729 B1 EP 0022729B1 EP 19800401062 EP19800401062 EP 19800401062 EP 80401062 A EP80401062 A EP 80401062A EP 0022729 B1 EP0022729 B1 EP 0022729B1
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EP
European Patent Office
Prior art keywords
jack
tripping
hydraulically
seat
operating system
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired
Application number
EP19800401062
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English (en)
French (fr)
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EP0022729A1 (de
Inventor
Jean-Paul Robert
Claude Pinet
Robert Jean
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Merlin Gerin SA
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Merlin Gerin SA
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Publication date
Application filed by Merlin Gerin SA filed Critical Merlin Gerin SA
Publication of EP0022729A1 publication Critical patent/EP0022729A1/de
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Publication of EP0022729B1 publication Critical patent/EP0022729B1/de
Expired legal-status Critical Current

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Classifications

    • H—ELECTRICITY
    • H01—ELECTRIC ELEMENTS
    • H01H—ELECTRIC SWITCHES; RELAYS; SELECTORS; EMERGENCY PROTECTIVE DEVICES
    • H01H33/00—High-tension or heavy-current switches with arc-extinguishing or arc-preventing means
    • H01H33/02—Details
    • H01H33/28—Power arrangements internal to the switch for operating the driving mechanism
    • H01H33/285—Power arrangements internal to the switch for operating the driving mechanism using electro-dynamic repulsion
    • H—ELECTRICITY
    • H01—ELECTRIC ELEMENTS
    • H01H—ELECTRIC SWITCHES; RELAYS; SELECTORS; EMERGENCY PROTECTIVE DEVICES
    • H01H33/00—High-tension or heavy-current switches with arc-extinguishing or arc-preventing means
    • H01H33/02—Details
    • H01H33/28—Power arrangements internal to the switch for operating the driving mechanism
    • H01H33/30—Power arrangements internal to the switch for operating the driving mechanism using fluid actuator
    • H01H33/34—Power arrangements internal to the switch for operating the driving mechanism using fluid actuator hydraulic
    • H—ELECTRICITY
    • H01—ELECTRIC ELEMENTS
    • H01H—ELECTRIC SWITCHES; RELAYS; SELECTORS; EMERGENCY PROTECTIVE DEVICES
    • H01H33/00—High-tension or heavy-current switches with arc-extinguishing or arc-preventing means
    • H01H33/02—Details
    • H01H33/28—Power arrangements internal to the switch for operating the driving mechanism
    • H01H33/30—Power arrangements internal to the switch for operating the driving mechanism using fluid actuator
    • H01H2033/308—Power arrangements internal to the switch for operating the driving mechanism using fluid actuator comprising control and pilot valves

Definitions

  • the propellant of a four-way hydraulic valve comprises a solenoid whose excitation causes the unidirectional movement of a movable closure element. This results in the actuation of a piston whose operating rod cooperates with a link mechanism to ensure the closing of the circuit breaker.
  • the opening of the circuit breaker occurs by means of tripping means separate from the interlocking valve, said means being formed by a tripping coil causing, in the event of excitation, unlocking of the link mechanism.
  • This device is complicated because it requires a double hydraulic and mechanical control to close and open the circuit breaker.
  • the movable element of the hydraulic valve is unstable in the open position, and a return spring ensures the return of said element to the closed position.
  • the thruster acts only in the direction of opening of the valve.
  • the object of the invention is to avoid the aforementioned drawbacks and to produce a reliable and enduring hydraulic control device, using a quick-response bistable hydraulic valve when the circuit breaker is engaged and tripped.
  • the supply duct of the accumulator is equipped in the vicinity of the second seat with an inlet nozzle of predetermined size for adjusting the engagement speed.
  • the discharge conduit for venting the cylinder contains an exhaust nozzle determining the tripping speed.
  • a drawer formed in said body of the valve is associated with the first and second seats in order to cooperate with the corresponding bearing faces of the shutter member respectively at the end of the engagement race and trigger, so as to increase the effect of the hydrodynamic support forces when closing said drawer, and the stability of the shutter member in the engaged and triggered position.
  • an anti-water hammer device in particular an oleopneumatic damper or a unidirectional nozzle, cooperates with the hydraulic circuit in the vicinity of said intake orifice to avoid internal overpressure of the valve oil during its displacement towards the engagement position.
  • said propellant element comprises an electrodynamic repulsion actuator with a movable conductive disc inserted in an axial air gap formed outside the valve body between two fixed engagement and release coils, the selective excitation by capacitor discharge causes the electrodynamic repulsion of the disc in a determined direction to ensure the crossing of the cylinder dead center towards the engaged or released position.
  • the propellant element of the obturator member comprises a hydraulic differential piston provided with two active faces sensitive to the pressure variation of the control oil contained in two elementary chambers, each equipped with an auxiliary valve. , such that the rapid opening of one of them causes the corresponding chamber to be placed under vacuum or in compression, followed by displacement of the differential piston in a determined direction.
  • the hydraulic valve designated by the general reference 10, comprises a fixed body 12 arranged between an electrodynamic actuator 14 and a jack 15 for controlling the tripping and engagement of the mechanism of a high voltage circuit breaker .
  • the actuator 14 comprises a bidirectional thruster with double axial air gap and electrodynamic repulsion of the Thomson type provided with a movable disc 16 interposed between two fixed engagement 18 and trigger 20 coils.
  • the disc 16 of conductive material is integral with an actuating rod 22 mounted with alternating sliding in a bore 24 of the body 12 with the interposition of an annular seal 26.
  • the valve 10 comprises a shutter member 28 mechanically coupled to the actuating rod 22, and capable of occupying two stable longitudinal positions at the end of the engagement and tripping travel respectively when the disc 16 is coupled against the coil 20 and the actuator coil 18 14.
  • the shutter member 28 comprises a cylinder 14.
  • the shutter member 28 comprises a coaxial hollow cylinder 30, of diameter greater than that of the rod 22, and sliding inside a central bore 32 of the body 12 provided with a annular groove 34 for housing a seal 36.
  • One 38 of the ends of the shutter cylinder 30 is cut in a bevel and cooperates in the locked position (fig.
  • the two seats 40, 48 of the body 12 are separated longitudinally from one another by a predetermined axial distance d 1 , and the bidirectional sliding stroke of the shutter member 28 between the two seats 40, 48 corresponds exactly to that of the disc 16 between the two coils 20, 18 of the actuator 14.
  • the flange 44 is provided, opposite the face 46, with an auxiliary face shaped as sparging 50 with a diameter greater than the central bore 32, and coming into abutment against the central section of the body 12 when the valve 10 is in the engaged position.
  • One 52 of the front faces of the body 12 pierced by the central bore 32 determines with the seat 48 adjacent a radial orifice 54 for admission of pressurized oil, in connection with an oleopneumatic accumulator 56 or another high-pressure oil reservoir via a supply conduit 58.
  • the flange 44 of the cylinder 30 comprises a plurality of holes 60 distributed circumferentially according to a crown of diameter smaller than that of the seat 48, and making the inlet orifice 54 communicate with the internal conduit 62 of the hollow cylinder 30 in the engagement position of the valve 10 for supplying the cylinder 15, the filling of which moves the movable piston 64 in the direction of arrow F and the rapid closing of the contacts of the circuit breaker.
  • the front face 66 opposite that 52 of the body 12, with a bore 32, forms with the seat 40 juxtaposed an exhaust orifice 68 in connection with a discharge duct 70 with a tank 72 at low pressure for venting of the jack 15 in the release position (fig. 3) of the valve 10.
  • the supply duct 58 is equipped with an inlet nozzle 74 of predetermined size for adjusting the speed of closing of the contacts, and the discharge duct 70 similarly includes an exhaust nozzle 76 which determines the opening speed of the contacts when the jack is vented 15.
  • the valve 10 is bistable and rests on one of the seats 40, 48, so as to selectively connect the actuator 15 either to the oleopneumatic accumulator 56 for switching on the circuit breaker and keeping the contacts in the closed position, or to the cover 72 for venting the jack 15 when the circuit breaker trips.
  • the latching position (fig. 1)
  • the shutter member 28 of the valve 10 comes into leaktight abutment on the seat 40 to close the exhaust port 68 towards the tank 72 and simultaneously open the intake port 54 oil under high pressure.
  • the release position (fig.3), the shutter member 28 engages with the seat 48 to close the intake port 54 and simultaneously open the exhaust port 68 for rapid emptying of the jack 15.
  • Each of the two engagement and tripping positions of the valve 10 is stable, and the passage from one to the other is caused by the displacement in translation of the disc 16 of the electrodynamic actuator 14.
  • the inlet 54 and exhaust 68 orifices are partially open and make the oleopneumatic accumulator 56 communicate with the tank 72.
  • the flow of oil expelled from the accumulator 56 towards the tank 72 is limited by the pressure drops in the supply duct 58, the inlet nozzle 74, the passage section SA of the oil in the orifice inlet 54, variable according to the position of the flange 44, the holes 60 and l e internal duct 62 of the shutter member 28.
  • the passage section SE of the oil in the exhaust orifice 68 varying in opposite direction from the intake section SA, the exhaust nozzle 76 and the duct repression 70.
  • FIG. 8 shows the variation of the resulting hydrodynamic forces F as a function of the position x for different decreasing values of the inlet nozzle 74 (curves l, II, III), and it can be seen that in the middle position of the valve (position 0) the forces F are practically zero.
  • This median position constitutes in a way a dead center passage, the crossing of which depends on the displacement force of the actuating rod 22 during the excitation of the electrodynamic actuator 14.
  • the main role of the latter is to ensure the sudden passage from neutral, and the hydrodynamic forces F then take over or add to the electrodynamic forces of repulsion of the disc 16 to apply the valve 10 to one of the seats 40, 48, and maintain it stably in this position. It has been found that the hydrodynamic forces F exerted on the valve 10 are generated when one of the sections SA and SE for the passage of the oil in the valve was close to the smallest of the sections for the passage of the hydraulic circuit between the accumulator 56 and tank 72, for example when the intake section SA corresponds to the section of the nozzle 74.
  • the curve is an optimum curve corresponding to a predetermined value of the intake nozzle 74 greater than that of the nozzle of the curve III in which the memory effect is likely to be zero in the event of rebound of the valve 10 when it comes to the corresponding seat 40, 48.
  • the tripping of the circuit breaker is controlled by the excitation of the tripping coil 20 of the actuator 14, in particular by means of a discharge of a capacitor causing the electrodynamic repulsion of the conductive disc 16 in the direction of the coil 18 and the displacement fast from the shutter member 28 to the opposite seat 48.
  • the shutter member 28 After passing neutral from the electrodynamic forces of the actuator 14 (fig. 2), the shutter member 28 is sucked in by the hydrodynamic forces engen drées in the decreasing section of admission SA of the hydraulic circuit at the level of the orifice 54 and comes to bear on the seat 48. This position 54 and comes to bear on the seat 48.
  • This position is stable when the diameter of the seat 48 is greater than that of the bore 32, and the inlet 54 and exhaust 68 ports are respectively closed and open for venting the jack 15 to the cover 72 causing the rapid opening of the contacts.
  • the resetting is carried out during the excitation of the engagement coil 18 which causes the electrodynamic repulsion of the disc 16 in the direction of the coil 20.
  • the translational travel of the disc 16 is identical to that of the shutter member 28, which after crossing the neutral position in the middle position (fig. 2) is urged into stable support on the seat 40 by the hydrodynamic forces generated in the decreasing exhaust section SE in the vicinity of the orifice 68.
  • the valve 10 is then found in the latching position shown in fig. 1.
  • An intermediate amplifier stage (not shown) can be arranged downstream of the jack to be controlled by the valve 10.
  • the shutter member 28 engages against the corresponding seat 48 or 40 at reduced speed thanks to two dampers 80, 82 (fig. 6 and 7) hydraulics active in the vicinity of the two triggering and latching positions, and integrated inside the body 12 of the valve 10.
  • the damper 80 comprises a shoulder 84 formed at the junction of the actuating rod 22 with the rim 44 of the cylinder 30, and playing the role of piston capable of sliding at the end of the triggering stroke in an annular groove 86 of the body 12, of diameter greater than that of the bore 24. The compression of the oil in the groove 86 brakes the moving element formed by the rod 22 and the shutter member 28 ensuring a slow arrival of the latter on the seat 48.
  • the damper 82 similarly includes a step 88 on the shoulder 50 of flange 44, and an annular groove 90 in al central bore 32 of the body 12.
  • the step 88 plays the role of oil compression piston in the groove 90 at the end of the engagement stroke and causes a rebound engagement of the member 28 on the seat 40.
  • valve 10 is equipped with a cylindrical drawer 100 associated with the seat 48 of the body 12, so as to cooperate with the flange 44 of the shutter member 28 at the end of the triggering stroke (FIG. 5) to increase the effect of hydrodynamic forces when closing the drawer 100. This results in better stability of the shutter member 28 in the release position, regardless of the size of the inlet nozzle 74.
  • the seat 48 on which is supported by the member 28 is located between the bore 24 and the slide 100.
  • the shoulder 50 of the flange 44 compresses the oil contained in the cavity 102 located between the drawer 100 and the inlet nozzle 74.
  • the latter is placed in communication with an oleopneumatic damper 104 with membrane 106, or other anti-water hammer accumulator whose small volume is overpressure relative to the pressure of the oil in the accumulator 56.
  • the rest of the operation is identical to that described with reference to FIGS. 1 and 3.
  • the oleopneumatic damper 104 is replaced by a unidirectional nozzle 110 inserted in the hydraulic circuit between the supply duct 58 of the accumulator 56 and the inlet orifice 54 of the cavity 102.
  • a spring 112 urges the nozzle 110 resting on a flange 114 of the drawer 100; in the event of overpressure of the oil in the cavity 102 occurring during the engagement, the radial displacement of the nozzle 110 against the spring 112 allows an expansion of the oil in a recess 116 and in the accumulator 56.
  • the two variants of figs. 4 to 7 can be fitted on the low pressure side with a cylindrical slide 120 formed in the body 12 between the exhaust orifice 68 and the seat 40 (fig. 9).
  • the end 38 of the closure member 28 cooperates with the slide 120 at the end of the interlocking stroke to increase the effect of the hydrodynamic forces and the stability of the valve 10 in the interlocking position.
  • the electrodynamic actuator 14 of the Thomson effect type with double coils 18, 20, for switching on and off control is replaced by a hydraulic device 200 with differential piston 202 for actuating the shutter member 28.
  • the same reference numerals designate parts which are identical or similar to those shown in FIGS. 1 to 9.
  • the hollow cylinder 30 of the shutter member 28 slidably mounted inside a bore 32 between two stable longitudinal positions at the end of the engagement and tripping travel.
  • One 38 of the ends of the cylindrical shutter member 28 is cut in a bevel and comes into engagement in the latching position (fig. 10) with the circular seat 40 to close the exhaust orifice 68 of the discharge duct 70 in conjunction with a low pressure tank (not shown).
  • the opposite end 42 of the cylinder 30 has a flange 44 with an active frustoconical face 46 cooperating in the release position (FIG.
  • the flange 44 comprises a plurality of holes 60 communicating the inlet port 54 with the internal conduit 62 of the hollow cylinder 30 in the engagement position of the valve 10 for supplying the actuator (not shown) for closing the contacts of the circuit breaker.
  • the end 42 of the cylinder 30 is connected by the actuating rod 22 to the differential control piston 202 capable of sliding in a fixed cylinder 204 of the body 12.
  • the piston 202 has two active faces 206, 208 cooperating with the opposite bottoms of the cylinder 204 to delimit two elementary chambers 210, 212 in communication with the high pressure accumulator by two supply conduits 214, 216.
  • the volume of chambers 210, 212 varies in opposite directions from one another according to the direction of movement of the differential piston 202 controlled by the depression of one of the chambers.
  • the shutter member 28 In the engagement position (fig. 10), the shutter member 28 is in stable abutment on the seat 40 after the chamber 210 of the hydraulic device 200 has been placed under vacuum. Triggering is controlled by placing the vacuum under pressure. another chamber 212 causing the differential piston 202 to translate to the right and the stop member 28 coming into abutment against the seat 48 (fig. 11), so as to close the intake orifice 54 and simultaneously open l 'exhaust port 68 for venting the cylinder.
  • FIGS. 12 to 16 represent four alternative embodiments using the principle of the differential piston 202 of the hydraulic control device 200, illustrated in FIGS. 11 and 12.
  • each elementary chamber 210, 212 is associated with an auxiliary rapid purge valve 220, 222 actuated by an electrodynamic propellant 224, 226 with Thomson effect.
  • Each thruster 224, 226 comprises a control coil 228, 230 disposed opposite a movable disc 232, 234 of conductive material, associated with a striker 236, 238 cooperating with the corresponding purge valve 220, 222.
  • each chamber 210, 212 is biased in the closed position by means of an elastic member, in particular a return spring 240, 242, which maintains the corresponding purge valve in sealed contact against a seat 243 , 245 as long as the propellant 224, 226 remains in the inactive de-excitation position of the coil 228, 230.
  • the supply line 214, 216 for high pressure oil from each chamber 210, 212 is provided with an intake nozzle 244 , 246, arranged opposite the purge valve 220, 222 with respect to the axial direction of the cylinder 204.
  • Each seat 243, 245 has a section greater than that of the corresponding nozzle 244, 246 and is connected by a discharge conduit to a low pressure compartment 250 in connection with the cover.
  • the operation of the hydraulic control device 200 according to FIG. 12 is as follows:
  • the circuit breaker is engaged after excitation of the control coil 228 of the thruster 224 with electrodynamic repulsion, the striker 236 of which opens the purge valve 220 for a predetermined time, for example of the order of a millisecond. This results in the decompression of the chamber 210 and the discharge of the oil contained in the chamber 210 to the compartment 250 at low pressure.
  • the differential piston 202 is then biased in axial translation in the direction of the arrow F i , and applies the shutter member 28 to the seat 40, so as to open the intake port 54 and simultaneously close the exhaust port 68.
  • the triggering is carried out by excitation of the coil 230 of the propellant 226 causing the opening of the purge valve 222 and the decompression of the chamber 212 whose oil is discharged towards the compartment 250 at low pressure.
  • the differential piston 202 is actuated in axial translation along the arrow F 2 until the closure member 28 engages against the seat 48 causing the admission orifice 54 to close and the simultaneous opening of the exhaust port 68.
  • the differential piston 202 is provided with a communication conduit of the two chambers 210, 212 allowing the elimination of one of the supply conduits 214, 216.
  • the structure of the rapid purge valves 220, 222 can be of any type, in particular with frustoconical or spherical bearing cooperating with the circular seats 243, 245.
  • the switching on and off commands result from the decompression of one of the chambers 210, 212, following an impulse shock from one of the strikers 236, 238 on the corresponding purge valve 220, 222 which remains open for a time very short.
  • the control energy of the thrusters 224, 226 is much lower than that necessary for the displacement of the shutter member 28 of the valve 10 according to FIGS. 1 to 9.
  • the supply lines 214, 216 of high pressure oil open into the opposite bottoms 252, 254 of the cylinder 204, in the vicinity of the purge valves 220, 222
  • Each of these valves has a drawer end, which closes the corresponding conduit 214, 216 when one of the coils 228, 230 of the thrusters 224, 226 is energized. Closure of the conduits 214, 216 from the start opening the purge valves 220, 2222 allows a saving of control oil contained in the oleopneumatic accumulator or other high pressure oil tank, and accelerates the decompression of the chambers 210, 212.
  • the seats 243, 245 of the purge valves 220, 222 are formed in the opposite bottoms 252, 254 of the cylinder 204.
  • the strikers 236, 238 of the electrodynamic thrusters 224, 226 move in opposite direction l '' from one another in a direction parallel to that of axial translation of the piston differential 202.
  • each purge valve 220, 222 comprises a first frustoconical portion 260 cooperating in the closed position with the corresponding seat 243, 245, a second intermediate lateral portion 262 of cylindrical shape capable of closing the supply duct 214, 216 of high pressure oil at the start of the valve opening stroke and a third cylindrical portion 264 in the shape of a piston with a diameter less than that of the intermediate portion 262.
  • Each bleed valve 220, 222 is provided with 'A plurality of holes 266 communicating the supply lines 214, 216 of high pressure oil with the chambers 210, 212 in the inactive position of the thrusters 224, 226 corresponding to the closing of the purge valves.
  • the piston of the third portion 264 moves into a central housing 268 of the low pressure compartment 250 connected to the tank.
  • a fixed O-ring 270 surrounds the piston 264 of each valve 220, 222, compensated and provides sealing between the housing 268 at low pressure and the chambers 210, 212 of the hydraulic device 200.
  • FIG. 14 The operation of the device of FIG. 14 is similar to that of FIG. 13, the only difference being the use of purge valves 220, 222 compensated, each having an end shaped as a piston 264 displaceable in the housing 268 at low pressure.
  • the differential piston 202 for controlling the bistable valve 10 forms an integral part of the closure member 28.
  • One 206 of the active faces of the differential piston is formed by a shoulder located in the central zone of the cylinder 30.
  • the other 208 active face of the differential piston is constituted by a solid cylindrical end piece 272 arranged opposite the end 38 of the cylinder 30, so as to slide in a bore 274 of the body 12.
  • the face 206 delimits the elementary chamber 210 formed in the body 12 between the discharge conduit 70 and the conduit 58, and in communication with the high pressure accumulator by the supply conduit 214 provided with the intake nozzle 244.
  • Decompression of the chamber 210 by the opening of the rapid purge ball valve 224 causes the shutter member 28 to be actuated towards the latching position (fig. 15).
  • the other face 208 delimits the second elementary chamber 212 arranged opposite the circuit breaker control cylinder, and in communication with the high pressure accumulator by the supply duct 216 with a nozzle 246.
  • a ball valve 226 for purging rapid is associated with chamber 212, the decompression of which when the purge valve 226 opens causes the shutter member 28 to engage with the seat 48, followed by tripping of the circuit breaker (fig. 16).

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  • Magnetically Actuated Valves (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Driving Mechanisms And Operating Circuits Of Arc-Extinguishing High-Tension Switches (AREA)

Claims (12)

1. Hydraulischer Antrieb eines dem Schaltmechanismus eines Hochspannungsschalters zugeordneten Zylinders zum Öffnen und Schliessen der Kontakte, der besteht aus :
- einem mit Drucköl gefüllten Speicher (56),
- einem unter schwächerem Druck stehenden Entlastungsraum (72) zur Entlastung des Zylinder- öles (15) bei der Ausschaltung,
­ einem Hydraulikventil (10) zur wahlweisen Verbindung des Zylinders (15) mit dem Speicher (56), zum Einschalten und Zurückhalten der Kontakte in der Schliesslage oder mit dem Entlastungsraum (72), zur Entlastung bei der Ausschaltung,
- Speise-(58) und Entlastleitungen (70) zur Verbindung des Ventiles bzw. mit dem Speicher (56) und dem Entlastungsraum (72),
- einem feststehenden Körper (12) mit einem nahe der Austrittsöffnung (68) der Entlastleitung (70) liegenden ersten Sitz (40) und mit einem nahe der Einlassöffnung (54) der Speiseleitung (58) liegenden zweiten Sitz (48), wobei die beiden Sitze (40, 48) gegeneinander mit einem vorbestimmten axialen Abstand versetzt sind,
- und einem Antriebsorgan (14, 200), das das Ventil zwischen den beiden Sitzen (40, 48) um den genannten Abstand zur Einschaltung oder Ausschaltung des Schalters, verstellen kann, wobei das Ventil (10) ein in einer Bohrung (32) des Körpers (12) verstellbares Abschlussorgan (28) aufweist, dadurch gekennzeichnet, dass das Abschlussorgan (28) des Ventiles (10) in den beiden Endstellungen am Ende der Einschaltungs- und der Ausschaltungsstrecke stabil ist, und dass das Abschlussorgan durch einen Hohlzylinder (30) gebildet ist, welcher besteht aus :
- einer ersten Auflagefläche (38), an einem Ende des Zylinders (30), die am Ende der Einschaltstrecke gegen den ersten zwischen den Entlastleitung (70) und der Zylinderleitung (62a) liegenden Sitz (40) in stabiler. Auflage kommt,
- einer zweiten Auflagefläche (42), an dem gegenüber liegenden Ende des Zylinders (30), die am Ende der Ausschetstrecke in stabiler Lage mit dem zweiten zwis'. 'n der Speiseleitung (58) und dem Antriebsorgan (14, 200) liegenden Sitz (48) zusammenarbeitet, wobei das Antriebsorgan mechanisch auf der Seite der zweiten Auflagefläche (42) am Zylinder (30) gekuppelt ist,
- und einer internen Leitung (62b), die an beiden Enden des Zylinders (30) durch gegenüber liegenden Öffnungen mündet, die je eine kleinere Abmessung als die des entsprechenden Sitzes (40, 48) besitzen.
2. Hydraulischer Antrieb eines Zylinders nach Anspruch 1, dadurch gekennzeichnet, dass die gegenüber liegenden Auflageflächen (38, 42) des Zylinders (30) mit den genannten ersten und zweiten Sitzen (40, 48) Öldurchgangsquerschnitte in den Speise- (54) oder Entlastungsöffnungen (68) bestimmen, welche Querschnitte sich im umgekehrten Sinn für einen bestimmten Bewegungssinn der Zylinderstrecke (30) ändern, wobei die Zylinderstrecke eine Zwischenstellung mit einem Totpunktübergang aufweist, dessen Übergang durch die vor den in den entsprechenden Durchgangsquerschnitten am Ende der Einschaltung oder Ausschaltung entstehenden hydrodynamischen Kräften wirkenden Antriebskräfte des Antriebsorganes (14, 200) bewirkt wird.
3. Hydraulischer Antrieb eines Zylinders nach Anspruch 1 oder 2, dadurch gekennzeichnet, dass die genannte Speiseleitung (58) des Speichers (56) in der Nähe des genannten zweiten Sitzes (48) eine Einlassdüse (74) mit vorbestimmtem Querschnitt zur Regelung der Einschaltgeschwindigkeit hat.
4. Hydraulischer Antrieb eines Zylinders nach Anspruch 1, 2 oder 3, dadurch gekennzeichnet, dass die genannte Entlastleitung (70) zur Entlastung des Zylinders (15) eine die Ausschaltgeschwindigkeit bestimmende Auslassdüse (76) hat.
5. Hydraulischer Antrieb eines Zylinders nach einem der Ansprüche 2 bis 4, dadurch gekennzeichnet, dass ein in dem Körper (12) des Ventiles (10) angeordneter Schieber (120, 100) dem ersten (40) und zweiten (48) Sitz zugeordnet ist, um am Ende der Einschalt- und Ausschaltstrecke mit den entsprechenden Auflageflächen (38, 42) des Abschlussorganes zusammenzuarbeiten, so dass die Wirkung der hydrodynamischen Auflagekräfte beim Schliessen des genannten Schiebers und die Stabilität des Abschlussorganes in Einschalt-und Ausschaltstellung vergrössert sind.
6. Hydraulischer Antrieb eines Zylinders nach Anspruch 5, dadurch gekennzeichnet, dass jeder Schieber (100, 120) bzw. zwischen dem zweiten Sitz (48) und der Speiseöffnung (5) in der Nähe der Ausschaltlage und zwischen dem ersten sitz (40) und der Entlastungsöffnung (68) in der Nähe der Ausschaltlage angeordnet ist.
7. Hydraulischer Antrieb eines Zylinders nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass eine Vorrichtung gegen Druckstösse, nämlich ein ölpneumatischer Stossdämpfer (104) oder eine Einrichtungsdüse (110) mit dem hydraulischen Kreis in der Nähe der genannten Speiseöffnung (54) zusammenarbeitet, um einen internen Ölüberdruck des Ventiles bei seiner Verschiebung nach der Ausschaltlage zu verhindern.
8. Hydraulischer Antrieb eines Zylinders nach irgendeinem der Ansprüche 2 bis 7, dadurch gekennzeichnet, dass das genannte Antriebsorgan einen elektrodynamischen Abstossantrieb (14) mit einer in einem axialen Luftspalt ausserhalb des Körpers (12) des Ventiles zwischen zwei feststehenden Einschalt- und Ausschaltspulen (18, 20) angeordneten beweglichen leitenden Scheibe (16) aufweist, wobei eine selective Speisung der Spulen durch Entladung eines Kondensators eine elektrodynamische Abstossung der Scheibe (16) in einer bestimmten Richtung zur Überschreitung des Totpunktes des Zylinders (30) nach der Ausschalt- oder Einschaltlage bewirkt.
9. Hydraulischer Antrieb eines Zylinders nach irgendeinem der Ansprüche 1 bis 7, dadurch gekennzeichnet, dass das Antriebsorgan (200) des Abschlussorganes (28) einen hydraulischen Differentialkolben (202) mit zwei aktiven Flächen (206, 208) aufweist, die auf die Druckänderung des in zwei Unterkammern (210, 212) enthaltenen Steuer- öls ansprechen, wobei jede Kammer ein Hilfsventil (220, 222) aufweist, so dass die Schnellöftnung von einem der Hilfsventile das Entlasten oder das Unter-Druck-Stellen der entsprechenden Kammer (210, 212) und die Verschiebung des Differentialkolbens (202) in einer bestimmten Richtung bewirkt.
10. Hydraulischer Antrieb eines Zylinders nach Anspruch 9, dadurch gekennzeichnet, dass jede Unterkammer (210, 212) durch eine Speiseleitung (214, 216) mit dem Speicher (56) verbunden ist, und dass jedes Hilfsventil (220, 222) mit einem elektrodynamischen Auslöser (224, 226) mit einem Abstosser (236, 238) zusammenarbeitet, um in aktiver Lage das Entlasten einer der Kammern (210, 212) durch Öffnung des entsprechenden Ventiles und Auslaufen des Öles nach einem mit dem Entlastungsraum (72) verbundenen Abteil (250) zu bewirken.
11. Hydraulischer Antrieb eines Zylinders nach Anspruch 10, dadurch gekennzeichnet, dass jedes Schnellentlast-Hilfsventil (220, 222), am Beginn seiner Öffnungsbewegung zum Abschliessen der Speiseleitung (214, 216) der entsprechenden Kammer (210, 212) ausgebildet ist.
12. Hydraulischer Antrieb eines Zylinders nach Anspruch 9, 10 oder 11, dadurch gekennzeichnet, dass der genannte Steuerdifferentialkolben (202) des bistabilen Ventils (10) zum Abschlussorgan (28) gehört, wobei eine der aktiven Kolbenflächen durch eine in der Mittelzone des Zylinders (30) gelegene Schulter (206) und die andere Fläche durch ein zylindrisches volles, gegenüber der ersten Auflagefläche (38) liegendes Endstück (272) gebildet ist.
EP19800401062 1979-07-16 1980-07-15 Bistabiles hydraulisches Ventil für die Steuerung eines Kolbens eines schnellen Hochspannungs-Leistungsschalters Expired EP0022729B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR7918757A FR2462015A1 (fr) 1979-07-16 1979-07-16 Clapet hydrolique bistable associe a un propulseur electrodynamique pour la commande d'un verin de disjoncteur rapide a haute tension
FR7918757 1979-07-16

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EP0022729A1 EP0022729A1 (de) 1981-01-21
EP0022729B1 true EP0022729B1 (de) 1983-02-16

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JPH0750799Y2 (ja) * 1987-10-14 1995-11-15 カシオ計算機株式会社 楽音位相同期装置
CN112503044B (zh) * 2020-03-20 2022-12-16 国网上海市电力公司 一种液压控制阀及液压操动机构

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US2765378A (en) * 1953-05-26 1956-10-02 Allis Chalmers Mfg Co Circuit breaker with hydraulic motor controlled by a hydraulically biased valve
SE321020B (de) * 1968-07-16 1970-02-23 Asea Ab
US3764944A (en) * 1972-07-06 1973-10-09 C Erven Spiral motor coil
US4118613A (en) * 1977-06-27 1978-10-03 General Electric Company Hydraulically-actuated operating system for an electric circuit breaker

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FR2462015B1 (de) 1982-01-22
EP0022729A1 (de) 1981-01-21
FR2462015A1 (fr) 1981-02-06
DE3062026D1 (en) 1983-03-24
JPS5615516A (en) 1981-02-14

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